Space coolers



June 28, 1966 R. R. HANSON ET AL SPACE COOLERS Original Filed April 10.1961 10 Sheets-Sheet 1 INVENTORS ROY R. HANSON 8 ELMER A. BRADENATTORNEY June 9 1965 R. R HANSON ETAL 3,258,197

SPACE COOLERS Original Filed April 10. 1961 10 Sheets-Sheet 2 INVENTORSROY R. HANSON a ELMER A. BRADEN ATTORNEY June 28, 1966 R. R. HANSON ETAL 3,

SPACE COOLERS Original Filed April 10. 1961 10 Sheets-Sheet 3 s R a O W3 N 5 N A mH R v: o R

ELMER A. BRADEN K M iv 49 E Q @7? ATTORNEY June 1966 R. R. HANSON ET AL3,258,197

SPACE COOLERS Original Filed April 10. 1961 l0 Sheets-Sheet 4 A A F r'\1 4 I k- INVENTORS ROY R. HANSON 8| 4 ELMER A. BRADEN ATTORNEY FIG. 7;%MJM%\ J1me 1966 R. R. HANSON ET AL 3,258,197

SPACE COOLERS Original Filed April 10. 1961 10 Sheets-Sheet 5 INVENTORSROY R. HANSON 8 ELMER A. BRADEN FIG. 6.

ATTORNEY June 28, 1966 R. R. HANSON ET AL 3,258,197

SPACE COOLERS 1O Sheets-Sheet 6 Original Filed April 1.0. 1961 INVENTORSROY R. HANSON 8 ELMER A. BRADEN ATTORNEY June 28, 1966 R. R. HANSON ETAL 3,258,197

SPACE COOLERS l0 Sheets-Sheet '7 Original Filed April 10, 1961 FIG. l9.

FIG. 20.

INVENTORS ROY R. HANSON 8 ELMER A. BRADEN ATTORNEY June 28, 1966 R. R.HANSON ETAL 3,258,197

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FIG. 22

ATTORNEY June 28, 1966 R. R. HANSON ET AL 3,258,197

SPACE COOLERS Original Filed April 10. 1961 10 Sheets-Sheet 9 INVENTORSROY R. HAN 8: ELMER A. B EN ATTORNEY June 28, 1966 R. R. HANSON ET AL3,258,197

SPACE COOLERS l0 Sheets-Sheet 10 Original Filed April 10. 1961 FIG. 29

FIG. 28

FIG.

FIG. 30

33 INVENTORS ROY R. HANSON a BY ELMER A. BRADEN FIG. 32

AT TORN EY United States Patent 3,258,197 SPACE COOLERS Roy R. Hanson,Maryland Heights, Mo., and Elmer A.

Braden, Springfield, llll., assignors of one-sixth to William H.Anderson, Glencoe, and one-fourth each to Joseph H. Schierman and GeorgeA. Blase, both of St. Louis, Mo.

Original application Apr. 10, 1961, Ser. No. 102,060, now Patent No.3,189,262, dated June 15, 1965. Divided and this application Mar. 24,1965, Ser. No. 442,341

6 Claims. (Cl. 230-147) This invention relates in general torefrigerating equipment and, more particularly, to space coolers. Thepresent application is a division of our copending application SerialNo. 102,060, filed April 10, 1961, and issued as United States PatentNo. 3,189,262.

It is a primary object of the present invention to provide a spacecooler employing a rotatable compressor housing having an evaporator anda condenser mounted on and rotatable therewith.

It is also an object of the present invention to provide a space coolerof the type stated in which the movement of the housing and relatedelements will produce all necessary circulation of air.

It is an additional object of the present invention to provide a spacecooler of the type stated which utilizes a novel rotary type compressor.

It is another object of the present invention to provide a device of thetype stated which can be easily, economically and compactly constructed.

It is a further object of the present invention to provide a spacecooler of the type stated which is compact and contains a minimum numberof moving parts.

It is also an object of the present invention to provide a space coolerhaving a unique type of control means which compensates for fluctuationsin speed and demand.

With the above and other objects in view, our invention resides in thenovel features of form, construction, arrangement, and combination ofparts presently described and pointed out in the claims.

In the accompanying drawings (ten sheets):

FIG. 1 is a rear elevational view of a rotary refrigeration machineconstructed in accordance with and embodying the present invention;

FIG. 2 is a sectional view taken along line 2-2 of FIG. 1;

FIGS. 3 and 4 are sectional views taken along lines 3-3 and 44,respectively, of FIG. 2;

FIG. 5 is a fragmentary sectional view taken along line 55 of FIG. 3;

FIG. 6 is a fragmentary sectional view taken along line 66 of FIG. 5;

FIG. 7 is a fragmentary sectional view taken along line 77 of FIG. 4;

FIG. 8 is a fragmentary sectional view taken along line 88 of FIG. 6;

FIG. 9 is a fragmentary sectional view taken along line 99 of FIG. 5;

FIGS. 10 to 16, inclusive, are diagrammatic views similar to FIG. 6 andshowing various operative positions of the compressor;

FIG. 17 is a wiring diagram showing a preferred control circuit forminga part of the present invention;

FIG. 18 is a fragmentary sectional view showing a modified form of thepresent invention;

FIGS. 19 and 20 are fragmentary sectional views taken along lines 19-19and 20-20, respectively of FIG. 18;

FIG. 21 is an end elevational view of a modified form of compressorconstructed in accordance with and embodying the present invention;

FIG. 22 is a horizontal sectional view taken along line 22-22 of FIG.21;

FIG. 23 is a transverse sectional view taken along line 2323 of FIG. 22;

FIG. 24 is a fragmentary sectional view taken along line 24-24 of FIG.23;

FIGS. 25 and 26 are transverse sectional views taken along lines 25-25and 26-26, respectively of FIG. 22;

FIG. 27 is a fragmentary sectional view taken along line 2727 of FIG.25; and

FIGS. 28 to 33, inclusive, are diagrammatic crosssectional views showingvarious operative positions of the compressor during a single cycle ofits operation.

Referring now in more detail and by reference characters to the drawingswhich illustrate practical embodiments of the present invention, Adesignates a space cooler comprising a support casting 1 integrallyprovided on one end with a split mounting hub 2 provided with aplurality of bracing ribs 3 which terminate in an enlarged annular ring4. Rigidly secured to the split hub 2 by means of bolts 5 is astationary rotor shaft 6 provided with an enlarged collar 7 having aneccentric shaft portion 8, the forward end of which is formed withanother collar portion 9 and a short stub portion 10. The hub 2 isinternally grooved for reception of an annular sealing ring 10 whichbears sealingwise against the shaft 6. Journaled on the stationary rotorshaft 6 by means of spaced aligned bearings 11, 12, is a rotatablecylindrical compressor housing 13 provided internally on one end with aretaining cap 14 for snug-fitting reception of the bearing 12. Securedto the housing 13 by means of bolts 15 adjacent the retaining cap 14 isa condenser support casting 16, the retaining cap 14, housing 13, andsupport casting 16 forming a V-shaped groove 17 for reception of anannular sealing ring 18. Rotatably mounted on the shaft 6 between thehub 2 and bearing 11 is a collar 19 peripherally grooved for receptionof a sealing ring 20 which bears sealingwise against a diametrallyreduced section 21 of the housing 13. Interposed between the collar 19and the hub 2 is a seal 21 and disposed between the bearing 11 andcollar 19 is an annular disc-like spring d which urges the collar 19against the seal 21.

Rigidly mounted on the reduced portion 21 adjacent the hub 2 is aconventional electro-magnetic clutch member 22 having coils in and aconductor ring 0 which is contacted by a stationary brush B mounted onthe support casting 1. Journaled on the reduced section 21 by means of abearing 23 is a pulley 24 having an annular flange 25 which extendsconcentrically around the clutch member 22 and includes fixed magneticrings 26, 26, adapted for electromagnetic inter-locking with the clutchmember 22, and trained around the-pulley 24 is a V-belt 27 whereby thepulley may be driven by a suitable prime mover (not shown). The clutchcoils m are connected in a control circuit as shown in FIG. 17 andpresently more fully described. It will, of course, be evident thatother types of clutch mechanisms can be employed if desired.

Rotatably mounted on the eccentric shaft portion 8 is a cylindricalcompressor rotor 27' split in the provision of a mounting block 28provided with a chordwise extending slot 28' which is aligned with atapped hole 29 :for reception of a locking screw 29'. Also formed in therotor 27' and disposed radially with respect to the housing 13 and incontact therewith is a slot 30 for slide-fitting reception of a thinfiat compressor vane 31, the outer radial end of which is integrallyprovided with opposed pins 32, 33, which snugly engage correspondingrecesses 34, 35, the recess 34 being formed in the retaining cap 14 landthe recess 35 being formed in the housing 13. Also for-med in theretaining cap 14 is an inlet port 36, and similarly formed in thehousing 13 opposite the inlet port 36 and slightly olfset therefrom, isan angularly inclined high pressure discharge passage 37 whichcommunicates through a check valve 38 to a short tube 39 located in acondenser inlet line 40. As seen by reference to FIG. 9, the check valve38 is formed of a resilient annular ring which normally bears againstthe wall of a cavity 41 and is disposed across the passage 37, the checkvalve 38 being split at 42 so as to permit a slight diametralcontraction of the valve 38 and resultant opening of the passage 37, allfor purposes presently more fully appearing.

Mounted on the condenser support plate 16 is a condenser 43 including anouter end plate 44 which is rigidly supported in spaced relation to theplate 16 by a series of air impeller vanes 45, and extending between theplates 16, 44, are radially inner and outer series of tubes 46, 47,

refrigerant will flow from one of the tubes 46 through one of the capmembers 50, through one of the tubes 47, through one of the cap members49, and then through the next succeeding tube 47, and so on, throughoutthe condenser unit 43.

Secured by means of bolts 51 to the outer peripheral portion 4 of thesupport casting 1 is an insulating plate 52 which is supported on thehub portion 53 of the condenser support plate 16 by means of a bearing54. Also secured to the hub portion 53 by means of bolts 55 is anevaporator support plate 56 provided with a series of axial fins 57which interfi-t between corresponding fins 58 on the insulator plate 52so as to provide a labyrinth seal. Mounted on the plate 56 is anevaporator 58 including an end plate 59 rigidly supported in spacedrelation to the plate 56 by radially extending air impeller vanes 60,

the end plate 59 being provided with a large central opening 61.Extending between the plates 56, 59, are radially inner and outer seriesof tubes 62, 63, provided with heat transfer fins 64 and bolted to theplates 56, 59, are cap members 65, 66, which provide successivecommunication between tubes 62, 63, in the same manner as that of thecondenser 43, previously described, so as to form a continuousevaporator line. Secured to the outer periphery of the heat insulatorplate 52 and enclosing the evaporator 58' is an air cooling chamber 67provided with a warm air inlet passage 68 aligned with the opening 61and formed on the outer periphery of the air cooling chamber 67 is acold air discharge duct 69. As best seen by reference to FIGS. 2 and 5,the condenser inlet line 40 communicates with the condenser 43 through aconduit 70 and the condenser discharge line 71 communicates with apassageway 72 in the hub portion 53 which, in turn, communicates with anevaporator inlet line 73 having a capillary tube 73' formed therein. Theevaporator discharge line 74 communicates with a passageway 75 in thehub portion 53 which, in turn, is open to the space 76 between the hubportion 53 and cap member 14, the space 76 communicating with thecompressor inlet port 36.

As shown in FIG. 17, the space cooler A is preferably operated incombination with a control circuit which includes a main switch s and athermostat T having a manually settable control knob k. Also includedwithin the circuit is a rheostat R, the sliding element 2 of which isshifted responsive to the movement of a governor G. The governor, whichmay be of any conventional design, is connected to the sliding element eof the rheostat R in such a manner that, as the speed of the prime moverincreases, a progressively larger amount of resistance is thrown intothe circuit so as to reduce the strength of the electrical couplingbetween the coils in of the electromagnetic clutch member 22 and themagnetic rings 26, 26. Consequently, as the speed of the prime moverincreases, there will be a greater degree of slippagebetween theelectro-magnetic clutch member 22 and the pulley 24.

Consequently, where the space cooler A is employed in connection with anautomobile and the primer mover is the automobile engine, the speedof-the compressor will remain substantially constant, notwithstandingwide. fluctuations in engine speed. The thermostat T and switch s will,obviously, be mounted within the interior of the automobile and can beadjusted to maintain any desired degree of temperature by appropriateadjustment of the knob 1:. Similarly, the entire unit can be turned onand off by appropriate manipulation of the switch s.

In use, the :clutch member 22 is normally disengaged and the belt-drivenpulley 24 is freely rotatable on the reduced portion 21 of the housing13. Upon engagement of the clutch member 22, power is transmitted to thehousing 13, causing it and the condenser 43 and evaporator 58 to rotatein unison. During such rotation, the vane 31 will assume intermediatepositions, such as shown in FIGS. 10 through 16, so as to compress therefrigerant in the chamber a formed by the rotor 27', the housing 13,and the cap member 14. During one full revolution of the housing 13, itcan be seen that the chamber a, which communicates with thepassage 37,gradually becomes smaller and smallerwhi-le the chamber b, whichcommunicates with the inlet port 36, gradually becomes larger andlarger. As the pressure within the chamber 0 reaches condenser pressure,the check valve 38 diametrally contracts so as to permit the compressedrefrigerant to pass into the tube 39 through the line 40, into theconduit 70, and into the condenser 43. The increasing volume of thechamber b provides a reduced pressure on the outlet side of theevaporator 58 so as to draw the refrigerant therefrom. As the housing 13and rotor 27' move from the relative positions shown in FIG. 10 to thatshown in FIG. 12, they will momentarily assume an intermediate position,such as shown in FIG. 11, wherein the ports, 36, 37, are passed acrossthe rotor 27'.

By reason of the fact that the condenser 43 and evaporator 58' rotaterapidly, the refrigerant liquid which is contained therein will, as aresult of centrifugal force, flow along those portions of the interiorsurfaces which are radially remote. Consequently, a substantial area ofthe coils will always be wetted by a rapidly flowing film of liquidrefrigerant and the K-factor of the system is, therefore, high.

Warm air is drawn axially through the inlet passage 68 and through theopening 61, being drawn therethrough by the air impeller vanes 60 whichforce the air radially outwardly across the evaporator 58' so as tobecome cooled, whereupon the cool air is discharged through the duct 69.Air is also drawn by the air impeller vanes 45 axially along and overthe housing-13 and is forced radially outwardly over the condenser 43 soas to provide a forced air cooling of the condenser 43.

Since small quantities of oil may occasionally leak from the bearings11, 12, the circulation of such oil through the unit is effectivelyreduced since any oil entering the chamber 4 1Will be collected in anoil trap [formed by the tube 39 and check valve 38 and is held thereinby the centrifugal force of the rotating housing 13.

It is also possible to provide a modified form of space cooler A, shownin FIGS. 18-20, similar to the space cooler A, previously described. Inthis form of the invention, a condenser 77 is provided with a supportcasting 78, outer end plate 79, inner and outer series of tubes 80, 8 1,and cap members 82, 83, all similar to, and interconnected in the samemanner as, the corresponding parts of the condenser 43, previouslydescribed. Rigidly mounted on the tubes 80, 8 1, is a series of spacedparallel annular heat dissipation disks 84, each provided with spacedholes through which the tubes 80, 81, extend, and surrounding the holes85, are upstruck annular flanges 86 which bear against and grip thetubes 80, 81. Spanning the distance between successive disks 84 arecircumferentially spaced, punched out, axially extending air impellervanes 87. The disks 84 are also each provided with a large centralopening 88 and a radially extending clearance slot 89 for reception ofinlet and outlet conduits 90, 91.

During assembly of the condenser 77, the holes 85 are of such size as topermit the disks 84 to be easily slipped on the tubes 80, 81, and thedisks 84 are held in spaced relation by the air impeller vanes 87. Oneof the conduits 90, 9 1, is then closed off and air under high pressureis introduced into the condenser 77, causing the tubes 80, 81, todiametrally expand a few thousandths of an inch into grip-formingengagement with the flanges 86, whereupon the tubes 80, 81, will remainsnugly secured in position. It will, of course, be evident that anevaporator for the space cooler A may also be constructed in the samemanner as the condenser 77.

It is also possible to provide a modified form of cornpressor C, asillustrated in FIGS. 21 to 31, inclusive, 1ncluding a stationarycylindrical compressor housing 92, which is integrally provided at oneend with a radially outwardly extending annular flange 93 and at itsother end with an integral flat end-wall 94, which, in turn, terminatesat its inner margin in an outwardly extending coaxial journal housing95. Rigidly seated in, and extending closurewise across, the interiorend of the journal housing 95 is a journal collar 96 provided on itsouter surface with an annular groove 97 which communicates with anoutwardly extending small-diameter port 98 drilled or otherwise formedin and extending through the journal housing 95. The journal collar 96is furthermore machined upon its inwardly presented face in common withthe inwardly presented face of the end-wall 94 so that these faces areprecisely coplanar or flush with each other and form an uninterruptedsmooth surface.

Secured, by a series ofbolts 99, upon and extending axially outwardlyfrom the annular flange 93 is an intermediate housing plate 100 which issealed against the annular flange 93 by an O-ring 101 and integrallyincludes a diametrally reduced cylindrical journal housing 102 which iscoaxial with the journal housing 95. Rigidly seated in and extendingclosurewise across the inner end of the journal housing 102 is a journalcollar 103 which is machined upon its inwardly presented face in commonwith the inwardly presented face of the housing plate 100 so that suchfaces are precisely coplanar and form a smooth uninterrupted surface.Also secured to the annular flange 93 in common with the housing plate100, by means of the bolts 99, is a cylindrical end-shell 104 which isalso sealed to the housing plate 100 by means of an O-ring 105. Theend-shell 104 is of substantially the same diametral size as thecompressor housing 92 and has a flat end-wall 106 which is spacedaxially outwardly from the end-wall of the journal housing 102 in theprovision of an enclosed chamber 107.

Mounted telescopically on the opposite end of the com pressor housing 92and extending axially over the journal housing 95 is a second end-shell108 which is sealed to the compressor housing 92 by means of an O-ring109. The end-shell 108 is integrally provided with a flat end-wall 110which is disposed in outwardly spaced parallel relation to the end-wall94 of the compressor housing 92 and is, in turn, integrally providedwith diametrally reduced sleeve 111 which fits snugly against thejournal housing 95 and is sealed thereto by means of an O-ring 11 2. Theend-shell 108 is held in place by means of a locking collar 113 which isthreadedly seated in the outer end of the journal housing 95 and, on itsinternal end, abuts against a sealing plate 114 which, in turn, isseated against an annular shoulder 115 formed in the journal housing 95.The locking collar 113 and the sealing plate 114 are both provided withcoaxial apertures 116, 117, respectively, all as best seen in FIG. 22.

Snugly seated 'within the journal housing 95 is a conventional ballbearing 118 which is pressed snugly against the outer end face of thejournal collar 96 by means of a pressure sleeve 1 19 which bears, at itsopposite end, against the sealing plate 114 and is sealed thereagainstby an O-ring .112. Similarly seated in the journal housing 102 and heldbetween the end-wall thereof and the outer face of the journal collar103 is a second conventional ball bearing 120. Formed integrally with,and projecting axially outwardly from, the journal collars 96, 103, areshaft elements 121, I122, which are respectively journaled in the ballbearings 1'18, 120, and the journal collars 9 6, 103, are furtherintegrally connected across the compressor housing 92 by means of aneccentric shaft 123, the centerline of which is parallel to, but spacedradially outwardly from, the common centerline of the shaft elements121, 122, the latter, of course, being coaxial with the journal housings95, 102. It should be noted, in this connection, that the journalcollars 96, 103, the shaft elements 121, 122, and the eccentric shaft123 may be assembled from separate elements or maybe machined from asingle piece of steel depending upon manufacturing convenience.

The shaft element 121 is turned down along its outer or left-hand end(reference being made to FIG. 22) in the provision of a terminal portion124, which projects loosely and freely through the aperture 117 and issplinecoupled into the shaft 125 of a conventional electric motor 126,the latter being supported by means of twolegged mounting frame 127,which is, in turn, secured by means of bolts to the end-shell 108.Secured upon the outer end of the terminal portion 124, by means of abolt 129, is a radial counterweight having a head flange v131 which isdisposed in radially spaced coaxial relation to the sleeve 111 of theend-shell 108.

Disposed loosely around the shaft element 121 within the journal housing95 is a spiral spring 132 which bears at one end against the ballbearing 118 and at its other end against a pressure plate 133, which, inturn, abuts facewise against a sealing ring 134 which is sealed to theshaft element 121 by means of an O-ring 112" and is pressed against thesealing plate 114, so as to retain lubricants within the journal housing95. Since it is desirable to use liquid lubricant within the journalhousing 95, the shaft element 121 is provided with a radially outwardlyprojecting tubular oil-scoop 135 which opens internally to an axial oilduct 135" bored lengthwise through the eccentric shaft 123.

The shaft element 122 is similarly turned down at its outer end in theprovision of a coaxial terminal portion 136 which projects through theend-wall of the ournal housing 102 and is externally threaded forreceiving a radial counterweight 137 which is held rigidly thereon bymeans of a locking nut 138. The counterweight 137 is integrally providedat its outer end with zigyead flange 139 which rotates freely within thechamber Rotatably mounted on the eccentric shaft 123 is a cylindricalcompressor rotor 140 having a radial split 141 which is held together bymeans of dowel pins 142 and screws 143 to facilitate assembly of therotor 140 upon the eccentric shaft 123. The rotor 140 is carefullymachined across its end faces and is of such axial length as to fitsnugly within the compressor housing 92 and bear slidingly against theinwardly presented end faces of the endwall 94 and housing plate 100.Moreover, the rotor 140 is provided with a slot 144 which extendsaxially thereacross from one end of the rotor to the other and islocated in non-radial eccentric relation to the eccentric shaft 123 forslide-fitting reception of a thin flat compressor vane 145, the outerend of which is cylindrically enlarged in the provision of an axialhingeknuckle 146 for receiving a hinge-pin 147 which extends across thetop of the compressor housing 92 and is seated at its opposite ends inthe end-wall 94 and the housing plate 100, respectively, so that thecompressor vane will be rockably supported within the compressor housing92. Thus, it will be apparent that as the eccentric shaft 123 rotatesaround the centerline of the shaft elements 121, 122, the rotor 140 willrotate upon the eccentric shaft 123 and will roll non-rotatively withinthe compressor housing 92. It will, of course,

7 be apparent by reference to FIG. 25 that the rotor 140 is of suchdiametral size that its outer cylindrical surface will glide tightly butnevertheless, smoothly over the interior cylindrical surface of thecompressor housing 92. In addition to this, the slot 144 is provided atits outer end with an axially extending semi-cylindrical groove 148which is intended to afford clearance against the hinge-knuckle 146 asthe rotor passes through the top of its stroke. Internally within theslot 144, the rotor 140 is provided with an axially extending U-shapedslot 149 which contains a complementarily-shaped sealing blade 150 whichbears against the flat face of the vane 145 to prevent pressurized gasesfrom passing down along the vane from the pressure side to the low sidethrough the slot 144. As will be seen by reference to FIG. 22, the axiallength of the vane 145 is precisely equal to the axial length of thecompressor housing 92, so that the end faces of the vane 145 will rockback-and-forth in gas-sealing operative contact against the inwardlypresented faces of the end-wall 94 and the housing-plate 100, also forthe purpose of preventing unauthorized leakage of refrigerant gas fromthe high side to the low side of the compresor C.

If it be assumed, for purposes of illustration herein, that the rotor140 will rotate in a counter-clockwise direction, that is to say, thedirection indicated by the arrow in FIG. 25, then the housing-plate 100is provided with a relatively large intake opening 151 located on thesuction side (i.e. the left-side as shown in FIG. 26) with respect tothe vane 145. Similarly, the end-wall 94 of the compressor housing 92 isprovided with a somewhat smaller discharge opening 152 located on thepressure side (i.e. right-side as shown in FIGS. 25 and 26) with respectto the vane 145. The intake opening 151 communicates with the chamber107 and the discharge opening 152 communicates with a chamber 153 formedby the end-shell 108 around the opposite end of the compressor housing92. The chambers 107 and 153 are respectively provided with a suction orintake line 154 and a pressure or discharge line 155 whch areconventionally connected to. the evaporator and condenser of arefrigeration system through conventional controls (not shown).

Clamped externally upon, and extending around, the portion of thejournal housing 95 which extends through the chamber 153 is a mountingring 156 which is integrally provided with a radially upwardly extendingflat, arcuate valve-plate 157 which is formed of resilient spring-steeland normally seats in closurewise relation across the discharge opening152, but is sufiiciently resilient to flex outwardly away fromclosurel-forming position under pressure of compressed refrigerant gaswhich intermittently flows outwardly from the compressor housing 92 asthe rotor 140 reaches the top of its stroke. The clamping ring 156 isprovided with an upturned stop-forming ear 158 located approximately inthe center of the lower margin of the valve-plate 157 so as to preventexcessive outward movement thereof, but nevertheless permittingsufiicient movement of the valve-plate 157 to allow unobstructed flow ofcompressed gas from the compressor housing '92 into the chamber 153.

In use, the motor 126 is energized and the eccentric shaft 123 rotated,thereby producing orbital movement of the rotor 140 and rocking movementof the vane 145. During such orbital movement, the rotor 140 and thevane 145 will move through the various positions shown in FIGS. 28 to33, inclusive, thereby drawing refrigerant gas through the intakeopening 151, compressing -it, and discharging it under pressure throughthe discharge opening 152, substantially in the same manner aspreviously described in conection with the compressor rotor 27'.

It should be understood that changes and modifications in the form,construction, arrangement, and combination of the several parts of thespace coolers may be made and substituted for those herein shown anddescribed without departing from the nature and principle ofourinvention.

Having thus described our invention, what we claim and desire to secureby Letters Patent is:

1. A compressor, said compressor comprising a stationary housing havinga cylindrical chamber, end walls afiixed to thehousing at its ends inclosure-forming relation to said cylindrical chamber, said end wallsbeing provided with opposed inlet and outlet ports located in arcuatelyspaced relation to each other, 'a rotatable rotor shaft opera-tivelyjournaled within said housing and being provided with a portioneccentric to the axis of rotation of said housing, a cylindrical rotorrotatably mounted on said eccentric portion and provided with an axiallyextending slot located of]? center therein, said rotor having end faceswhich are in slidable abutment with said end walls, said rotor includingcomplementary first and second rotor segments, said first segment beingdefined by said slot and a diametrally extending line whichperpendicularly intersects said slot, and a vane rockably secured tosaid housing between the inlet and outlet ports, said vane being adaptedfor slide-fitting reception within the slot for forming a fluid barrierbetween said ports, said v-ane being in spaced parallel relation to theaxis of said eccentric portion.

2. A compressor comprising a stationary housing having a cylindricalchamber, end walls aflixed to the housing across the ends of thecylindrical chamber, said end walls being provided with opposed inletand outlet ports located in arcuately spaced relation to each other, arotatable rotor shaft operatively journaled within said housing andbeing provided with a portion eccentric to the axis of rotation of saidhousing, a rotor rotatably mounted on said eccentric portion and havingend faces which are in slidable abutment with said end walls, acompressor vane rockably secured to said housing between the inlet andoutlet ports, said compressor vane being adapted for slidefittingreception within the rotor eccentric of the axis thereof for forming afluid barrier between said ports, and a resilient closure plate carriedby said housing and normally biased across said outlet port insealing-wise engagement with the end wall in which said outlet port islocated, said closure plate being adapted to flex outwardly away fromthe outlet port at a preselected pressure so as to allow pressurizedfluid to escape from said cylindrical chamber.

3. A compressor, said compressor comprising a stationary housing havinga cylindrical chamber, circular spaced parallel end walls atfixd to thehousing across the ends of said cylindrical chamber and having centrallylocated axially aligned cylindrical bores formed therein, said end wallsbeing provided with opposed inlet and outlet ports located in arcuatelyspaced relation to each other, a rotatable rotor shaft operativelyjournaled within said housing and being provided with annular journalcollars having cylindrical surfaces which ride in said cylindrical boresin sealing-wise engagement therewith, an eccentric portion interposedbetween and carried by said journal collars in outwardly spaced relationto the axis of said rotor shaft, a rotor rotatably mounted on saideccentric portion, a compressor vane adapted for slide-fitting receptionwithin said rotor, and means on the outer radial end of said vane forrockably securing it to said housing between the inlet and outlet ports.

4. A compressor, said compressor comprising a stationary housing havinga cylindrical chamber, end walls affixed to the housing across the endsof said cylindrical chamber, said end walls being provided with opposedinlet and outlet ports located in arcuately spaced relation to eachother, a rotatable rotor shaft operatively journaled within said housingand being provided with a portion eccentric to the axis of rotation ofsaid housing, a cylindrical rotor rotatably mounted on the eccentricportion and having its ends in slidable engagement with said end Walls,the rotor being formed from two rotor segments which are secured to eachother around said eccentric portion of said rotor shaft, a compressorvane hingedly secured to said housing between said inlet and outletports along the cylindrical surface of said cylindrical chamber, saidvane being adapted for slide-fitting reception within said rotor so asto form a fluid barrier between said ports, and means on the outerradial end of said vane for rockably securing it to said housing betweenthe inlet and outlet ports.

5. A compressor comprising a stationary housing having a cylindricalchamber, first and second circular end walls aflixed to said housingacross the ends of said cylindrical chamber, said end walls havingopposed parallel planar surfaces and being centrally provided withaxially aligned cylindrical bores, said walls being provided with inletand outlet ports, respectively, located in arcuately spaced relation toeach other, said end walls being provided in outwardly spaced relationto their planar surfaces with bearings concentrically located with saidbores, a shaft having concentric shaft elements operatively mounted insaid bearings, said shaft elements terminating in journal collars havingcylindrical surfaces which ride in said cylindrical bores insealing-wise engagement therewith, said journal collars having planarend faces which rotate in coplanar relation with the planar surfaces ofsaid end walls, an eccentric portion carried between and by said journalcollars and extending across said cylindrical chamber, the centerline ofsaid eccentric portion being parallel to and spaced radially outwardlyfrom the centerline of the shaft elements, a cylindrical rotor rotatablymounted on said eccentric portion and having planar ends in slidableengagement with said end faces of the journal collars and said opposedplanar surfaces of the end walls, a vane slidably mounted in said rotorand being rockably connected along one axial margin to the chamberbetween said outlet port and inlet port whereby as said rotor rotateswith respect :to the housing said vane also slides within the rotor androcks with respect to the housing, one of said shaft elements projectingoutwardly beyond the chamber, and prime mover means operativelyconnected to said projecting end for'rotatin-g the shaft.

6. A compressor comprising a stationary housing having a cylindricalchamber, first and second parallel circular end walls affixed to saidhousing in closurewise relation to said chamber, said first and secondend walls being provided with opposed inlet and outlet ports,respectively, located in arcu-ately spaced relation to each other, saidchamber also being provided at its opposite ends with bearingsconcentrically located with said cylindrical chamber, a shaft havingconcentric shaft elements operatively mounted in said bearings and alsohaving an eccentric portion extending across said cylindrical chamber,the centerline of said eccentric portion being parallel to and spacedradially outwardly from the centerline of the shaft elements, acylindrical rotor rotatably mounted on said eccentric portion, a vaneslidably mounted in said rotor and being rockably connected along oneaxial margin to the chamber between said outlet port and inlet portwhereby as said rotor rotates with respect to the housing said vane alsoslides within the arcuate member and rocks with respect to the housing,one of said shaft elements projecting outwardly beyond the chamber,means associated with said second end wall for forming an encloseddischarge chamber around the outlet port, a resilient closure platecarried within said discharge chamber and normally biased against saidsecond end wall in surrounding closurewise relation to said outlet port,said closure plate being adapted to flex outwardly away from the outletport at a preselected pressure so as to allow pressurized fluid toescape from said cylindrical chamber, means associated with said firstend wall for forming an inlet chamber around the inlet port, said inletport establishing communication between the cylindical chamber and inletchamber, and prime mover means operatively connected to said projectingend for rotating the shaft.

References Cited by the Examiner UNITED STATES PATENTS 236,173 1/1881Mellor 103-432 1,969,999 8/ 1934 Outhbert 230147 2,493,148 1/ 1950Kiekh-aefer 103132 3,001,384 9/1961 Hanson et al 230- 3,189,262 6/ 1965Hanson et al 230l40 FOREIGN PATENTS 453,983 4/ 1913 France.

426,755 3/ 1926 Germany.

2,909 1914 Great Britain.

MARK NEWMAN, Primary Examiner.

WILBUR I. GOODLIN, Examiner.

1. A COMPRESSOR, SAID COMPRESSOR COMPRISING A STATIONARY HOUSING HAVINGA CYLINDRICAL CHAMBER, ENDS WALLS AFFIXED TO THE HOUSING AT ITS ENDS INCLOSURE-FOMING RELATION TO SAID CYLINDRICAL CHAMBER, SAID END WALLSBEING PROVIDED WITH OPPOSED INLET AND OUTLET PORTS LOCATED IN ARCUATELYSPACED RELATION TO EACH OTHER, A ROTATABLE ROTOR SHAFT OPERATIVELYJOURNALED WITHIN SAID HOUSING AND BEING PROVIDED WITH A PORTIONECCENTRIC TO THE AXIS OF ROTATION OF SAID HOUSING, A CYLINDRICAL ROTORROTATABLY MOUNTED ON SAID ECCENTRIC PORTION AND PROVIDED WITH AN AXIALLYEXTENDING SLOT LOCATED OFF CENTER THEREIN, SAID ROTOR HAVING END FACESWHICH ARE IN SLIDABLE ABUTMENT WITH SAID END WALLS, SAID ROTOR INCLUDINGCOMPLEMENTARY FIRST AND SECOND ROTOR SEGMENTS, SAID FIRST SEGMENT BEINGDEFINED BY SAID SLOT AND A DIAMETRALLY EXTENDING LINE WHICHPERPENDICULARLY INTERSECTS SAID SLOTS, AND A VANE ROCKABLY SECURED TOSAID HOUSING BETWEEN THE INLET AND OUTLET PORTS, SAID VANE BEING ADAPTEDFOR SLIDE-FITTING RECEPTION WITHIN THE SLOT FOR FORMING A FLUID BARRIERBETWEEN SAID PORTS, SAID VANE BEING IN SPACED PARALLEL RELATION TO THEAXIS OF SAID ECCENTRIC PORTION.